Metering device



y 1950 w. J. HUGHES 2,509,685

METERING DEVICE Filed July 9, 1347 2 Sheets-Sheet 1 I IN VEN TOR.

i 'a tented May METERING DEVICE Walter J. Hughes, Chicago, 111., assignor to Infilco Incorporated, Chicago, 11]., a corporation of Delaware Application July 9, 1947, Serial No. 759,838

9 Claims.

This invention relates to a metering device adapted to convert a pressure utilized in the measurement of any condition to a speed of rotation of a shaft which varies as the square root of the pressure utilized in the measurement.

This invention is particularly applicable to a meter for measuring fluid flows and adapted to convert a pressure differential, such as that existing between the mouth and throat of a Venturi tube, to a speed of rotation of a shaft directly proportional to the rate of flow.

Another aspect, or object, of my invention is to provide a power driven shaft of variable speed, the speed varying proportionally to the square root of a pressure to be measured.

While many applications of my invention will be apparent to those skilled in the art, it is primarily designed for use in connection with liquid treating systems, such as water conditioning plants and the like. Most measurements in such a plant are secured from a pressure differential existing between two points in the system, and when rate of flow is being measured it is well known that the pressure varies as the square of the flow. Many means have been suggested for extracting the square root of such a pressure differential, in order to get readings, or work done, which is directly proportional to the rate of flow. My apparatus has particular utility when it is desired to use a motor to eifect some control in such a plant, such as a motor driving a lime feeder in connection with a water softening plant. Obviously in such a case the rate of operation should be directly proportional to the rate of flow, and it is therefore necessary to provide a means for driving the machine to be operated, such as the lime feeder, according to the square root of the pressure differential. It is an object of my invention to utilize an ordinary motor rotating at a substantially constant speed and provide a mechanism which automatically converts such a constant speed of rotation to an angular velocity of the driven shaft which varies as the square root of the pressure differential utilized in such measurements.

These and other objects of my invention will be apparent from the drawings and detailed description, and in which:

Figure 1 represents a partial cross-sectional view of a simple form of my invention with belts partially removed;

Figure 2 is a side view of the idler pulley mounting;

Figure 3 is a vertical cross-sectional view of another embodiment of my invention.

The apparatus shown in Figure 1 is a simple form of my invention. As indicated above I utilize a substantially constant speed motor [0,

which for convenience is mounted upon a suitable base plate II. It can be noted that while the motor Ill operates continuously, and at substantially constant speed, it is not necessary that the motor always operate at the same speed as' tion or work desired, as the torque which is transmitted by the output shaft can be of any magnitude. A shaft E2 of the rotor of the motor is directly connected to a shaft l3 by any suitable coupling M. The free end of the shaft I3 is journaled in a quill shaft, or sleeve, l5 which in turn is journaled in a suitable bearing i6 carried by the transmission case I'i. A driving pulley I8 is pinned to the shaft it as shown. A belt 19 (best shown in Figure 2) passes over driving pulley l8, idler pulley 2B, and a variable pitch pulley 2| (such as shown in enlarged view on the left hand side of Figure 3, pulley IN).

The idler pulley 20 is suitably journaled in an arm 25 which is pivotally mounted on the base plate II by any suitable means such as pin 26. The arm 25 is positioned by means of a reversible motor 2?, and drive screw 28. The screw 28 is threaded into a nut 29 which is mounted on the arm 25, whereby the arm 25 is moved angularly by the reversible motor 2'5. The wiring and operation of the motor 21 will be described in detail hereafter.

The variable pitch pulley 2! is pinned to a shaft 35 rotatably journaled in a bearing 36, which may be mounted in an arm 32 carried by the transmission casing H. Also mounted on the shaft 35 is a fixed diameter driving pulley 38, as shown. A belt 39 connects the fixed diameter pulley 38 to a pulley it which is rigidly secured to the sleeve, or quill shaft, it. A planetary arm 4| is likewise pinned to the sleeve to rotate therewith. The arm fill carries a pair of shafts 42 on which are mounted planetary gears 43 and with said gears forms the speed varying or reaction member of the planetary gear train. A sun gear as is keyed to the shaft l3, meshing with the planetary gears An output shaft 56' is axailly aligned in the transmission casing H, with the shaft 53. A ring gear 5| is pinned to the output shaft 5% and meshes with the planetary gears 33. The shaft 50 can be utilized to perform work, such as the operation of a chemical feeder which it is desired to control in direct proportion to the rate of flow being measured, or to operate a telemetering device or the like. Also mounted on the shaft 50 is a bevel gear 52, with which meshes a bevel pinion 53. The bevel pinion 5. 3 is pinned to a shaft 54 journaled in bearing 55. The other end of the shaft 56 carries an arm 5% pinned thereto. A pair of bell crank arms 5'! are pivoted on the member 56. The bell cranks ill, have weights 58 at their outer ends and their inner ends 59 bear upwardly against a thrust bearing 60. Thus the fly ball governor, which comprises the arm 56 and the bell cranks til, rotates at a speed directly proportional to that of the output shaft 59. The centrifugal effect of the governor exerts a force upwardly which varies as the square of the velocity.

Opposing. the upward thrust of the governor assembly is a bellows" it, the upper end of which is rigidly attached to a base I i, which preferably is carriedby the' transmission casing H. To the lower end of the bellows is fixed a thrust rod l2 on which'is mounted the thrust'bearing t0. Also mounted at the lower end of the bellows is a contactor arm is whichis directly connected by conductor i i to source of power L1, the free end of the. contactor arm is bearing a contact member Associated with the contact member l5.

are two contacts "it and ill which are connected by means of conductors it and itfrespectively, to the reversible motor 27. The motor 2i is also o nected t ur Q new r Lzib me qij i ductor. 80.

he. bellows it: is q m e .9 qoedu 1.

connecting to a source of pressure by which operation of my apparatusis to be controlled. This source of res ure ay e a. dir t c nn ct n to, a pressuradifferential creating device, but pref;

erably, willbea source of controlled air pressure varying directly as the pressure difterential, such s. e ppar tu sh n n m ent am-s a p ication, Serial No. 630,506, m June as, 194.6.

If desired, a gaugeal can also be connected to.

the pressure conduit 82, as shown,

It is obvious that when the thrust of the b e 1- the. contact 15 will be disengaged from. both contacts 1E and ii and the circuit to motor;

21. will therefore be broken. When. such a condition arises the, position of the idler pu r.

ley will remain constant. and'the speed of rota,- tiort of the. output shaft, Eli will likewise remain constant. When the condition being measured varies, the pressure within thev bellows it will either increase or decrease, causing. the balance between the thrust of the bellows and thrust from the governor to be upsetywhereby the contact F5. will engage either. contact, itv or H, completing a circuitto the motor Zlto operateit in one direction or the other until anew speed of transmission outputand also governor speed sets up a new condition of equilibrium. It will be obvious that as the position of the. idler arm 25 is changed, the tension laced, on the belt l9, by the positioning of the idler pulley 2t, automatically changes the pitch radius of the variable pitch pulley 21', thereby changing the relative movement between the sun ear Atand the planetary arm ii, thus automatically vary ing the speed of rotation of the output shaft 59.

In onesize of the apparatus of my inventionI use sun and planetary gears 44 and 43 of 1 inch in diameter, a ring gear 5! of 3 inches in diameter, a sun shaft pulley 18 of 1% inches in diameter, a pulley 38 of 1.68 inches in diameter, a pulley it on the sleeve of 3 /2 inches in diameter, and an automatic variable pitch pulley having a pitch diameter of between 1% inches and 3 inches. In such an apparatus, assuming a motor speed of 1750 R. P. M. when the variable pitch pulley is at a diameter of 3.35 inches the planet arm rotates at a speed of 432 R. P. M., while if the diameter of the variable pitch pulley is changed to 1.8 inches then the planet arm rotates at {$05 It. B, M.which figures can be readily computed by those skilled in the art. The sun gear it however rotates at a constant velocity, a it is directly connected to the motor l0. As is well known in the art, the speed of rotation of the ring gear Si is determined by the relative velocities of the sun gear M and the planetary arm ll a in epicyclic gear trains. and the output shaft or ring gear speed can be varied from zero to maximum by proper relation of speeds of sun gear and planet arm. The variation in the angular position of the idler pulley arm 25. which directly controls the speed of rotation of the planetary arm, indirectly controls the angular velocity of the ouput shaft 50. Through. the switch arrangement shown, the speed of the output shaft 56 is controlled so, that the thrust of the governor mechanismjust balances the thrust of the bellows iii, thereby providing a speed of rotation of the output shaft varying; as the square root of the pressure. If the pressure is derived from a Venturi tube, or the like, then my apparatus provides a speed of rotation which variesdirectly as the flow being measured.

It is well known that in an,epicycl;ic gear train having a first member driven ata substantially: constant speed and a second member driven atv variable speeds, the outputmember. can be controlled to run at-speeds: from zero to; any desired maximum by a relatively small change in speed of the second; member. movement of; the idler pulley. arm, with a relatively small change in; the pitch diameter of the variable pitch pulley, provides; a; considerable change in thespeed' of the output, shaft, Specifically, in the above example, achange in the diameter of the variable pitch pulley of about 1 inches (from 1.8" to 3.35") provides a, change invelocity of from about 400 R P. to about 800 R. P. M. It is; obvious that one utilizing the principle of my invention need; only; determinethe maximumspeeds desiredinthe output shaft, andthen it is a,matter-o f easyzcomputation to determinethe necessary'sizes of gears andpulleys.

The embodimentshown in Figure; iii-works: on the same principle, as, thatshown Figures 1 and2. In this form .thaplanetary gearing is contained in atransmission casing ltlLthe. sun shaft.

I!!! being journaled in suitablebearings: Hi2. and N13. The sun gear, ltd is keyed to the inner end of the shaft, as, shown. Fixed diameter input pulley I05 iskeyed-to the outer end of the sun shaft IE1 and is drivenby amotor, not shown, through means of a .belt;- m6. A variable pitch pulley Ill! is directly connected tothe-input pul ley Hi5 as shown. The belt H18. passes Over the variable pitch: pulley It'l', amidler pulley, not shown, and pulley H5. In this embodiment the idler pulley is mountedandoperated-the same as in Figure 1, and for sake of simplicityis not shownin Figure 3, although, its operation will be readily understood bythose ,skilledin, the art.

Thus, a relatively small;

The pulley H5 is keyed to a shaft H6 and preferably is of the wide type in order to ermit axial displacement of the belt I08 as the pitch diameter of pulley I01 varies. The shaft H6 is suitably journaled in bearings H1. A pinion H8 is keyed to the inner end of the shaft I I6, as shown. A relatively large annular gear H9 meshes with pinion H8 and is suitably journaled in bearing I20 which surrounds the sun shaft IN. The annular gear H9 serves as a planetary arm but is driven directly by the pinion H8 at a variable speed and like the arm M in the embodiment of my invention shown in Figure 1, forms the speed varying or reaction member of the planetary gear train.

The output shaft I30 is coaxially aligned with the sun shaft IOI terminating close to the sun gear I04 as shown. The output shaft I30 is journaled in suitable bearings I3I, and at its inner end carries a pinion I32 which is keyed thereto. Rotatably mounted on the output shaft I30 is a rotatable arm I33, which rotates freely with respect to the output shaft I30. A pair of diametrically opposed bearings I34 and I35 are provided in the rotatable arm I33.

The annular gear H9 is provided with a pair of diametrically spaced bearings I21 and I22, which are located a radial distance from the center of rotation of the gear equal to that of the bearings I34 and I35 from their center of rotation. A connecting shaft I40 has one end journaled in bearing I21 of the annular gear H9 and the other end journaled in the bearing I34 of the arm I33. A second connecting shaft I4I has one end journaled in bearing I22 of annular gear H9 and the other end journaled in bearing I35 of the arm 33. Thereby the arm I33 is rotated at the same speed as the annular gear H9. A gear M2 is keyed to shaft I40 and meshes with sun gear i04,while a second gear I43 is keyed to the shaft M and meshes with the gear I32 on the output shaft I30. Similarly, a gear M4 is keyed to the shaft MI and meshes with sun gear i 4 and a second gear I45, also keyed to the same shaft, mes-hes with gear I32. Thus the sun gear E5 drives the planetary gears I42 and I44, respectively, and these in turn drive the gears I43 and 145, respectively, the latter meshing with gear Q32 to drive output shaft I30. However, the angular velocity of the gears I42 and I44 does not depend upon the velocity of sun gear I04, which is constant, but upon the relative motion, or relative angular velocity, of the sun gear I04 and the large annular gear H9. The velocity of the annular gear H9 in turn depends upon the pitch of the pulley I01 which is adjusted by the positioning of an idler pulley, such as I8 of Figure 2.

The governor arrangement shown in Figure 3 differs somewhat in detail from that shown in Figure 1. A shaft I50 is journaled in suitable bearings I5I. A bevel gear I52 is keyed to the inner end of the shaft I50 and meshes with a bevel pinion 153, keyed to the output shaft I30. An arm member I54 is pinned to the shaft I58 and carries a pair of pivotally mounted and weighted arms I55. Governor arms I55 engage the bearing member I56 which is rotatably mounted with respect to a connecting link I51 which is pinned to the lever arm I58. Lever arm I58 carries a contact 15, as shown.

Opposing the thrust of the weighted governor arms I55, which operates downwardly in this embodiment, is the force of a controlled air pressure acting upwardly in a diaphragm chamber I65, which is mounted above the lever arm I58. The diaphragm chamber preferably will comprise three sections: A casing portion I66 mounted on the transmission casing I00; an intermediate member I61; and an upper member I68. Clamped between the three members are two diaphragms I69 and I10, respectively, the effective area of the upper diaphragm I10 being in excess of that of the lower diaphragm I69. Due to the difference of the effective areas of the diaphragms the pressure in the intermediate chamber formed by the section I61 provides a net force operating upwardly. The two diaphragms I69 and I10 are held in spaced relationship by a spacing member I1I. Centering plate I12 of the lower diaphragm !69 carries a link I13 which is pinned to the lever arm I58. The outer diaphragm plate I14 of the upper diaphragm I10 is partially supported by a spring I15, th tension of which can be regulated by a suitable adjusting screw 16. The force of the spring I15 should be adjusted so as to balance the effect of the weight of parts attached to the diaphragms, their centering plates and spacer bar, so that at zero position (when a motor driving the belt I08 is at rest and there is no pressure in the pressure chamber 665) the contact 15 would be intermediate the two contact points 16 and 11.

The operation of this embodiment will be readily understood. When the centrifugal force derived from the governor mechanism exactly balances the net force from the air pressure within the diaphragm, or pressure, chamber I65, the setting of the idler pulley (such as IS in Figure 2) will remain constant and the relative velocity of the sun gear I04 and the annular gear I I9 will remain constant. As the pressure changes, the balance between the two forces is up-set causing a circuit to the reversible motor to be closed through contact 15, whereby the idler arm 25 of Figure 2, is moved, which changes the radius of the variable pitch pulley I08, and thus changes the relative velocities between the sun gear Hi4 and the annular gear H9. It is obvious to those skilled in the art that the velocity of the output shaft I38 will vary from zero to maximum speeds according to the difference in velocity between the sun gear I04 and the annular gear H8. As the centrifugal force of the governor mechanism varies as the square of the velocity, the speed of rotation of the output shaft I30 will necessarily vary according to the square root of the pressure exerted upon the diaphragm. In the process of measuring a flow through a flow system, which I utilize to illustrate my-invention, the pressure in the chamber I65 will vary as the square of the flow to be measured, thus providing a speed of rotation of shaft I30 directly proportional to the rate of flow to be measured.

It will be obvious to those skilled in the art that my apparatus provides a device for controlling the output speed of a shaft directly pro-.- portional to a flow or, which is saying the same thing, varying as the square root of a pressure differential used in the measurement of the flow. It is also obvious that the power delivered by output shaft I 30 can be of any desired magnitude, as my apparatus works equally Well with large or small motors. Manifestly many modifications and variations of the invention herein before set forth may be made by persons skilled in the art without departing from the spirit and scope thereof. Also it will be manifest that the apparatus of my invention could be applied to many situations and the appended claims therefore are 7 not to be limited. to measurement of a fluid flow, which has been used to illustrate the workings of my invention.

I claim:

1. In an apparatus of the class described, an epicyclic gear train having a drive member rotatable at a constant speed, a driven output member, and a reaction member rotatable at variable speeds to obtain speeds of the output member varying from zero to maximum, motor means for driving said drive member and said reaction member, means for varying the speed of rotation of said reaction member, a pressure responsive member, 9, centrifugal governor driven by the output member, and adapted to react against the force exerted by said pressure responsive member, and switching means operating by changes in force exerted by said pressure responsive member and controlling the operation of the said means for varying the speed of rotation of said reaction member.

2. In an apparatus of the class described, an epicyclic gear train having a driving member, a reaction member, and a driven output member, means for driving said driving member at a constant speed, means for driving said reaction member at a variable speed, a pressure responsive member, a centrifugal governor, a drive connection from said output member to said governor,

said governor being adapted to react against the force exerted by said pressure responsive member, and switching means operating by lack of balance between the force of the pressure responsive member and the force of the governor for controlling the speed of said reaction memher.

3. In a metering device, an epicyclic gear train having a driving member, a reaction member, and a driven output member, a constant speed motor directly connected to said driving member, whereby said driving member is rotated at a constant speed, means including a variable pitch pulley connecting said motor to the reaction member, a positioning means controlling the pitch of said variable pitch pulley, a reversible motor operating said positioning means, a pressure responsive member adapted to be actuated by the pressure proportionate to a rate of flow to be measured, a centrifugal governor driven by the output member and adapted to react against and balance the force exerted by said pressure responsive member, and a switch operated by unbalance of said pressure responsive member and governor and controlling the flow of power to said reversible motor.

4. A metering apparatus for rotating an output member at a speed varying according to the square root of variations in a force comprising n epicyclic gear train having a driving member, a reaction member, and a driven output member, a constant speed motor connected to said driving member, a variable speed drive connection from said motor to said reaction member, a pressure responsive member positionable by variations in said force, a governor driven by said output member and adapted to react against and balance the force of said pressure responsive member, and switching mean-s operated by a lack of balance between the force of said pressure member and said governor and controlling the operation of said variable speed drive connection.

5. In an apparatus of the type described, an epicyclic gear train including a sun gear, means adapted to drive said sun gear at substantially constant speed, a planetary arm forming a reaction member for the gear train, means includ-- ing a variable pitch pulley member for driving said planetary arm, means for changing the pitch of said variable pitch pulley member to vary the speed of said planetary arm, planetary gears carried by said planetary arm and meshing with said sun gear, output means driven by said planetary gears, a governor driven by said output means, a pressure responsive member adapted to be connected to a source of pressure and to balance the force of said governor, and a switch operated by lack of balance between the governor and the pressure responsive member, said switch being connected to operate said means for changing r the pitch of said variable pitch pulley.

6. In an apparatus of the type described, a motor operable at substantially constant speed, a sun gear driven by said motor, a variable pitch pulley, a planetary arm driven by said variable pitch pulley and forming a reaction member for the planetary gear train, planetary gears meshing with said sun gear and mounted on said planetary arm, an output gear driven by said planetary gears, a pressure responsive member adapted to be connected to a source of pressure, a governor, a drive connection from said output gear to said governor, the thrust of said governor opposing the thrust of said pressure responsive member, a switch operated by the unbalance of the opposing forces of said pressure responsive member and said governor, a, reversible motor connected to said switch and controlled thereby, and means operable to vary the pitch of said variable pitch pulley, said means including a movable idler pulley positionable by operation of said reversible motor.

7. In a power transmission device adapted to provide a variable output speed directly proportional to the flow of a liquid, a pressure responsive device, means adapted to supply pressure to said pressure'responsive device proportional to the square of the flow of a liquid, a motor, an epicyclic gear train having a driving member driven by said motor, a driven output member and a reaction member, a variable speed drive connection from said motor to said reaction member, means for varying the speed of said variable speed drive connection, and means controlling operation of said speed varying means including a governor rotatably driven by said output member, an operative connection between said governor and said pressure responsive device, and operative to actuate said speed varying means, upon unbalance of said pressur responsive device and governor, to vary the speed of said variable speed drive connection until a new balance has been established between said governor and said pressure responsive device.

8. In a power transmission device adapted to provide a variable output speed directly proportional to the flow of a liquid, a pressure responsive device, means adapted to supply pressure to said pressure responsive device proportional to the square of the how of a liquid, a motor, an epicyclic gear train having a driving member driven by said motor, a driven output member and a reaction member, a variable speed drive connection from said motor to said reaction member, speed varying means including a reversible motor for varying the speed of said variable speed drive connection, a control switch movable to one position to connect said reversible motor to rotate in one direction and movable to another position to connect said reversible motor to operate in a reverse direction, a centrifugal governor rotatably driven by said output member and connected to said pressure responsive device to oppose the force exerted thereby, an operative connection from said governor and pressure responsive device to said switch, to move said switch to its several operative positions upon unbalance between said pressure responsive device and governor, to connect said reversible motor to operate in one direction or another.

9. In a power transmission device adapted to provide a variable output speed directl proportional to the flow of a liquid, a pressure responsive device, means adapted to supply pressure to said pressure responsive devic proportional to the square of the flow of a liquid, a motor, an epicyclic gear train having a driving member driven by said motor, a driven output member and a reaction member, a variable speed drive connection from said motor to said reaction member including a variable pitch pulley, a reversible motor, means driven by said reversible motor to vary the pitch of said pulley, a centrifugal govm Number ernor rotatably driven by said output member and opposed by the force exerted by said pressure responsive device, a control circuit for said reversible motor, a switch in said control circuit and positionable to connect said circuit to cause said reversible motor to rotat in one direction or another, and means operatively connecting said switch with said pressure responsive device and governor, to operate said switch upon changes in pressure on said pressure responsive device causing unbalance between said governor and pressure responsive device.

WALTER J. HUGHES.

REFERENCES CITED The following references are of record in the file of this patent:

FOREIGN PATENTS Country Date 822,087 France Sept. 13, 1937 

